JPH08312751A - Damper device for direct clutch - Google Patents

Abstract

(57) [Summary] [Purpose] To reduce the size of a damper device for a direct coupling clutch, facilitate manufacturing, and improve durability. [Structure] A drive plate (input member) 6 of a direct coupling clutch 4 and an intermediate plate (intermediate member) 12 for transmitting torque by outer and inner damper springs (outer diameter side and inner diameter side spring bodies) 8 and 10 are connected. Rivet (first connecting portion) 18 for connecting the intermediate plate 12 and the driven plate (output member) 14 (second connecting portion)
22 to the outer and inner damper springs 8 and 10
It is provided at the middle portion in the radial direction of.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an input member of a direct coupling clutch built in a torque converter, via an outer diameter side spring body, an inner diameter side spring body, and an intermediate member for transmitting torque between the spring bodies. The present invention relates to a damper device for a direct coupling clutch that is elastically linked to an output member in the rotational direction.

[0002]

2. Description of the Related Art A torque converter is provided with a direct coupling clutch that directly couples an input member for inputting an output of an engine and an output member for outputting to a speed change mechanism in order to improve fuel economy. When the direct coupling clutch is engaged, a large shock is generated due to a rapid change in torque, and when traveling in the direct coupling state, vibration is generated due to torque fluctuation of the engine.

Therefore, conventionally, a damper mechanism provided with an outer diameter side spring body, an inner diameter side spring body, and an intermediate member is provided in order to absorb the sudden torque change and to improve the vibration characteristic during the direct connection running. Are known.

In order to improve the vibration characteristics during direct coupling, it is effective to reduce the spring constant of the spring body. However, at the same time, it is necessary to handle the maximum input torque from the engine. Setting the spring constant simply low makes it difficult to handle large inputs. Therefore, by combining a plurality of springs in multiple stages, a low spring constant is set in the low input torque region and a high spring constant is set in the high input torque region.

Conventionally, all the individual springs of the damper mechanism have been arranged in parallel, but in recent years, springs have also been proposed in which the springs are arranged in series in order to realize low spring characteristics.

For example, Japanese Patent Publication No. 62-7412 discloses that
Disclosed is a damper device for a direct coupling clutch, which is provided with two kinds of outer and inner spring bodies in the radial direction and is arranged so that all of these spring bodies act in series with respect to an input torque.

[0007]

However, when the damper device disclosed in the above Japanese Patent Publication No. 62-7412 is adopted, for example, the length of the torque converter in the rotation axis direction becomes large, and the device is There is a problem that it becomes large.

The present invention has been made to solve the above-mentioned conventional problems, and provides a damper device for a direct coupling clutch, which is capable of downsizing the device, facilitating its manufacture, and improving its durability. To aim.

[0009]

According to the present invention, an input member of a direct coupling clutch built in a torque converter includes an outer diameter side spring body, an inner diameter side spring body, and an intermediate member for transmitting torque between the spring bodies. In the damper device of the direct coupling clutch elastically linked to the output member in the rotation direction, the first connecting portion between the input member and the intermediate member, and the second connecting portion between the intermediate member and the output member are provided. The above-mentioned object is achieved by arranging the outer-diameter side spring body and the inner-diameter side spring body in the radial intermediate portion.

According to the present invention, the output member has a third connecting portion to the next transmission member, and the third connecting portion is arranged near the intermediate portion between the outer diameter side spring body and the inner diameter side spring body. As a result, the above-mentioned object is achieved in the same manner.

According to the present invention, the first connecting portion between the input member and the intermediate member has a stopper portion for restricting the outer diameter side spring body from bending more than a predetermined amount, and the intermediate member and the intermediate member are provided. The second connection part with the output member has the stopper part for restricting the inner diameter side spring body from being bent by a predetermined amount or more, thereby achieving the same object.

Further, according to the present invention, the output member is a press-formed product having a bent portion formed, and the bent portion of the output member is used to form a third connecting portion from the output member to the next transmission member. By being configured, the above-mentioned object is achieved in the same manner.

It should be noted that the "connecting portion" is not limited to one that is completely fixedly connected by, for example, a rivet or the like.
It is assumed that rivets and the like include, for example, those that are movable in the long hole and that are connected to each other with a certain "play". Further, in addition to those in which two members are directly connected, those in which they are indirectly connected through another member such as a spring body are included.

[0014]

The input member of the direct coupling clutch built in the torque converter is elastic in the rotational direction with the output member via the outer diameter side spring body, the inner diameter side spring body and the intermediate member for transmitting torque between the spring bodies. Be linked together. Here, in the present invention, the first connecting portion between the input member and the intermediate member and the second connecting portion between the intermediate member and the output member are radially intermediate between the outer diameter side spring body and the inner diameter side spring body. It is located in the section.

Therefore, when the damper device according to the present invention is applied to, for example, a torque converter, the portion radially narrowed between the front cover and the turbine runner due to the curvature of the turbine runner is radially outer and inner circumferential sides. It becomes possible to arrange the two spring bodies on the outer diameter side and the inner diameter side in a relatively vacant portion of the above, and to arrange the first and second connecting portions in the narrow portion between them. As a result, the space can be effectively used especially in the radial direction, and the length of the entire torque converter device in the rotation axis direction can be minimized.

When the third connecting portion from the output member to the next transmission member is arranged in the vicinity of the intermediate portion between the outer diameter side spring body and the inner diameter side spring body, the output is transmitted to the next transmission member. Since it is not necessary to form a connecting portion with the member, the shape of the component positioned on the inner diameter side of the inner diameter side spring body is simplified, and the space can be effectively used.

The first member of the input member and the intermediate member
The connecting portion has a stopper portion that restricts the outer diameter side spring body from bending by a predetermined amount or more, and the second connecting portion between the intermediate member and the output member has the inner diameter side spring body by a predetermined amount or more. When the stopper is provided so as to prevent the spring from bending, when the direct coupling clutch is directly coupled and torque is input, it is possible to prevent excessive torque from acting on the spring body. The durability of can be improved.

Further, the output member is a press-formed product in which a bent portion is formed, and the bent portion of the output member is used to form a third connecting portion from the output member to the next transmission member. In such a case, it becomes easy to manufacture these members, and at the same time, the required rigidity can be secured at low cost.

[0019]

Embodiments of the present invention will now be described in detail with reference to the drawings.

1 to 3 show a damper device for a direct coupling clutch to which the present invention is applied.

FIG. 1 is a partially cutaway front view showing a damper device for a direct coupling clutch of a torque converter according to the present invention, and FIG. 2 is a sectional view taken along line II-II thereof. 3 is an enlarged vertical sectional view showing the upper half of the torque converter.

In the damper device for the direct coupling clutch of this embodiment, the drive plate (input member) 6 of the direct coupling clutch 4 built in the torque converter 2 includes the outer damper spring (outer diameter side spring body) 8 and the inner damper. A driven plate (output member) 1 is provided via a spring (inner diameter side spring body) 10 and an intermediate plate (intermediate member) 12 that transmits torque between the damper springs 8 and 10.
4 is elastically linked with 4 in the direction of rotation.

A rivet (first connecting portion) 18 for fixing the drive plate 6 to the lock-up piston 16 (also serving as a clutch plate) and a rivet (second for fixing the intermediate plate 12 and the spring guide plate 20). The connecting portion) 22 is arranged at a radially intermediate portion between the outer damper spring 8 and the inner damper spring 10.

That is, as shown in FIG. 3, between the front cover 24 and the turbine runner 26 of the torque converter 2, a portion narrowed due to the curved shape of the turbine runner 26 is radially inward and outward. The outer damper spring 8 and the inner damper spring 10 are arranged in wide portions corresponding to the circumferential side, and the rivets 18 and 22 constituting the first and second connecting portions are arranged in the narrow portion therebetween. Therefore, the length of the output shaft (not shown) in the axial direction is shortened, and the size of the device is reduced.

Further, in FIG. 3, the lock-up piston 16 is connected to the clutch surface 2 of the front cover 24 when directly connected.
8 has a friction plate 30 that abuts. Further, the flange portion 32 below the lockup piston 16 is slidably mounted on the bearing portion 36 of the turbine hub 34 and is sealed by a seal 38.

The driven plate 14 is a press-molded product, and the bent portion 40 is formed by bending the lower portion vertically. The bent portion 40 is provided with a spline 42, and the spline 42 engages with the spline portion 44 of the turbine hub 34 (next transmission member).
It constitutes a third connecting portion.

A spline 46 is provided below the turbine hub 34 and is engaged with an input shaft to a transmission mechanism (not shown).

Further, as shown in FIG. 7, the intermediate plate 12 has a plurality of elongated holes 48 which are elongated in an arc shape.
have. Through the elongated hole portion 48, the rivet 18 locks the drive plate 6 into the lockup piston 16
It is fixed to. The rivet 18 can move only within the range of the slot 48.

Further, as shown in FIG. 8, the driven plate 14 has four protrusions 50 on the circumference and a notch 52 opened on one side between them. The rivet 22 can move only within the cutout 52.

The operation of this embodiment will be described below.

When the lock-up piston 16 moves to the axially directly connected side (left side in FIG. 3) and its friction plate 30 comes into contact with the clutch surface 28 on the inner surface of the front cover 24 of the torque converter 2, the engine (not shown) is driven. The rotation is directly transmitted through the direct coupling clutch 4 and is in the direct coupling state.
At this time, an impulsive torque fluctuation from the lock-up piston 16 acts on the turbine hub 34 side, but this torque fluctuation is absorbed by the damper device according to the present invention as described below.

First, the torque that has entered the lock-up piston 16 is transmitted from the drive plate 6 integrated by the rivet 18 to the intermediate plate 12 via the outer damper spring 8.

In FIG. 1, if the drive plate 6 rotates counterclockwise, for example, the drive plate 6 pushes one end 8a of the outer damper spring 8 and the other end 8b of the outer damper spring 8 pushes the intermediate plate 12. It is for pushing. At this time, the lockup piston 16
The rivet 18 for fixing the drive plate 6 and the drive plate 6 moves only in the long hole portion 48 of the intermediate plate 12. When the rivet 18 comes into contact with the end of the elongated hole portion 48, the lock-up piston 16, the drive plate 6 and the intermediate plate 12 move as a unit.

Therefore, the rivet 18 plays the role of a stopper so that the outer damper spring 8 does not bend more than a certain amount.

Next, the intermediate plate 12 and the spring guide plate 2 which are integrated via the rivet 22.
0 pushes one end 10a of the inner damper spring 10,
Therefore, the other end 10b of the inner damper spring 10 pushes the driven plate 14. As a result, the torque is transmitted to the driven plate 14.

At this time, the rivet 22 moves only within the range of the notch 52 between the protrusions 50 of the driven plate 14. After the rivet 22 contacts the protrusion 50, the intermediate plate 12, the spring guide plate 20, and the driven plate 14 move integrally. That is, the rivet 22 functions as a stopper.

As described above, since the rivets 18 and 22 are used as stoppers, the structure is simplified and the manufacturing is facilitated, and it is possible to prevent excessive torque from acting on the springs, thus improving durability. Can be made.

The outer damper spring 8 is arranged on the outermost peripheral side, so that the stroke amount can be increased. or,
Outer damper spring 8 and inner damper spring 10
Since they are arranged in series, the spring constant can be reduced and the shock can be sufficiently absorbed.

The damper springs 8 shown in FIGS.
It demonstrates using the graph which shows the twist characteristic of No. 10.

Here, the twist angle θ is shown in FIGS. 6 (a) and 6 (b).
As shown in, the angle at which the spring bends when the torque T acts on the arc-shaped spring. The smaller the spring constant is (the lower the spring is), the larger the torsion angle θ becomes with respect to the smaller torque.

In the case of FIG. 4, the outer torsion spring 8 is greatly reduced in spring and the inner damper spring 10 is slightly reduced in spring, thereby enlarging the composite torsion angle θ.

In the example of FIG. 5, the outer damper spring 8 is made slightly lower in spring, and the inner damper spring 10 is made significantly lower in spring to enlarge the combined torsion angle θ.

By properly designing the respective springs in this way, it is possible to achieve a lower composite torsional spring. That is, the combined torsion angle θ is enlarged, and the maximum torsion torque that can be received by both damper springs 8 and 10 can be secured sufficiently large.

Therefore, since the composite torsional characteristic can be made low in spring, the range where the direct drive can be used can be expanded to the range where the engine speed is low. As a result, it is possible to directly drive the vehicle in a region where the vehicle has traveled by torque transmission by the fluid from the torque converter instead of directly connecting the vehicle, so that it is possible to improve fuel efficiency.

The torque transmitted to the driven plate 14 is transmitted from the spline 42 provided in the bent portion 40 below the driven plate 14 to the turbine hub 3 in FIG.
It is transmitted to the turbine hub 34 via the four spline portions 44. Then, the torque transmitted up to this point is finally output from the spline 46 of the turbine hub 34 to an input shaft (not shown) to the transmission mechanism.

Here, the driven plate 14 is shown in FIG.
It does not have the arcuate long hole shape as shown in FIG. 8B, but has the notch 52 opened to the outside as shown in FIG. 8A as described above. In the case of the long hole shape as shown in FIG. 8B, the portion h in the figure is required to be about 3 times the plate thickness, and the space in the radial direction increases. However, with the shape of this embodiment shown in FIG. 8A, the projection 50 does not impair the function of the stopper of the rivet 22, and a sufficient rivet arrangement space (arrangement space of the second connecting portion) is secured. be able to.

Further, since the bent portion 40 of the driven plate 14 is used as a constituent element of the third connecting portion to the turbine hub 34 which is the next transmission member, the driven plate 14 can be manufactured as a press-formed product. This makes it possible to facilitate manufacturing, and obtain necessary rigidity.

Next, another embodiment of the present invention will be described.

FIG. 9 is a vertical sectional view showing an upper half of a torque converter equipped with a direct coupling clutch according to another embodiment.

This embodiment differs from the previous embodiment in the location where torque is transmitted from the driven plate 114 to the turbine hub 134.

That is, in this embodiment, the driven plate 1
14 does not have a bent portion 40 as shown in FIG. Instead, the upper portion 114a extends slightly curved toward the turbine runner 126. A claw 160 is provided outside the central portion of the turbine runner 126. This claw 160 is the upper part 11 of the driven plate 114.
4a is engaged and torque is transmitted from there.

Since the structure other than this is the same as that of the previous embodiment, only the same parts in the drawing are given the same reference numerals in the last two digits, and duplicate explanations are omitted.

When the spline portion 44 is provided as in the previous embodiment, the bearing portion 36 of the lockup piston 16 is arranged further inside (inner diameter side), so that the inner peripheral diameter of the lockup piston 16 becomes smaller. It was getting smaller.

However, in this embodiment, the turbine hub 1
Torque transmission to the turbine runner 12 near the middle of the outer and inner damper springs 108 and 110.
This is done by engaging with 6. Therefore, it is not necessary to form the spline portion 144 on the turbine hub 134, and a large inner diameter of the lockup piston 116 can be secured.

Further, it is possible to more effectively use the space such that the inner diameter side damper spring 110 can be made larger. Therefore, in this embodiment, an unnecessarily increased axial dimension due to an increase in the deformation amount when the lock-up piston 16 shown in the previous embodiment moves, and controllability when switching between the direct connection state and the non-direct connection state, etc. The deterioration can be suppressed.

[0056]

As described above, according to the present invention,
The entire length of the torque converter device in the direction of the rotation axis can be minimized, the device can be downsized, and the space can be effectively used.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view showing a damper device for a direct coupling clutch according to the present invention.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a vertical cross-sectional view showing the upper half of the torque converter equipped with the direct coupling clutch according to the present embodiment.

FIG. 4 is a diagram showing a torsion characteristic of a spring body according to the present embodiment.

FIG. 5 is a diagram showing the torsional characteristics of the spring body according to the present embodiment.

FIG. 6 is a diagram showing a twist angle.

FIG. 7 is a front view showing the shape of the intermediate plate.

FIG. 8 is a schematic front view for comparatively explaining the action of the cutout portion of the driven plate.

FIG. 9 is a longitudinal sectional view showing an upper half of a torque converter equipped with a direct coupling clutch showing another embodiment according to the present embodiment.

[Explanation of symbols]

 2 ... Torque converter 4 ... Direct coupling clutch 6 ... Drive plate 8 ... Outer damper spring 10 ... Inner damper spring 12 ... Intermediate plate 14 ... Driven plate 16 ... Lock-up piston 18, 22 ... Rivet 20 ... Spring guide plate 26 ... Turbine runner 34 … Turbine hub 40… Bending part

Claims (4)

[Claims] 1. An input member of a direct coupling clutch built into a torque converter, an output member and a rotating direction via an outer diameter side spring body, an inner diameter side spring body, and an intermediate member for transmitting torque between the spring bodies. In a damper device for a direct-coupling clutch elastically linked with each other, a first connecting portion between the input member and the intermediate member, and a second connecting portion between the intermediate member and the output member include an outer diameter side spring body and an inner diameter side. A damper device for a direct coupling clutch, wherein the damper device is arranged at an intermediate portion of a side spring body in a radial direction. 2. The output member according to claim 1, wherein the output member includes a third connecting portion to the next transmission member, and the third connecting portion is near the intermediate portion of the outer diameter side spring body and the inner diameter side spring body. The damper device for the direct coupling clutch, which is characterized by being arranged. 3. The intermediate member according to claim 1, wherein the first connecting portion between the input member and the intermediate member has a stopper portion for restricting the outer diameter side spring body from bending by a predetermined amount or more. A damper device for a direct coupling clutch, wherein a second connecting portion between the output member and the output member has a stopper portion that restricts the inner diameter side spring body from bending by a predetermined amount or more. 4. The third connection from the output member to the next transmission member according to claim 1, wherein the output member is a press-formed product in which a bent portion is formed, and the bent portion of the output member is used. A damper device for a direct coupling clutch, characterized in that the parts are configured.